JP2003056584A - Dynamic characteristics measurement device for ball bearing - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a measurement device, capable of evaluating a bearing on thermal characteristics with high accuracy and ease, by controlling radiated amount with high accuracy and ease, and quantitatively considering the radiated amount. SOLUTION: This measurement device, measuring the characteristics of a bearing 103 to be tested, is provided with a line heater/cooler 133 for controlling the radiated amount of the bearing 103 to be tested, while the bearing 103 to be tested is operating. Continuous testing can be made, without the need for stopping the operation of the bearing 103 to be tested, in changing the radiating amount of the bearing 103 to be tested, as in a conventional technique; thus, testing efficiency can be improved.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement in a measuring device capable of measuring dynamic characteristics of rolling bearings such as dynamic torque.

[0002]

2. Description of the Related Art Even in a rolling bearing having a good lubrication condition, some friction loss occurs during operation, so that the temperature of the bearing rises due to heat generation corresponding to the friction loss. Here, the bearing temperature is an important factor that determines various performances (torque, seizure, material characteristics, etc.), and is determined from the balance between the heat generation amount and the heat radiation amount. The heat generation amount is determined by the internal specifications and dimensions of the bearing, bearing name number, lubrication method, etc., but the heat radiation amount is determined by the heat dissipation area of the bearing, environmental temperature, environmental conditions such as heat dissipation from the pedestal. . In other words, when performing a bearing rotation temperature rise test, it is necessary to set the amount of heat radiation according to the operating environment.

Quantitatively grasping the relationship between the bearing temperature, the amount of heat generated by the bearing, and the amount of heat radiated is equivalent to grasping the thermal characteristics according to the operating environment of the bearing, which is an extremely important issue in designing the bearing. Can be said. Here, when the heat generated in the bearing and the heat radiation from the bearing seat are in an equilibrium state, that is, in a steady state in which the bearing temperature is stable, the heat generation amount of the bearing becomes equal to the heat radiation amount from the bearing. Therefore, the following formula is established. T × ω = Qr (1) ω = 2πN / 60 (2) Qr = qr × Ar (3) where T: bearing friction torque (N · m) ω: bearing angular velocity (rad / s) N: bearing rotational speed ^(min -l) qr: heat radiation amount (W) qr: heat flow density ^(W / m 2) Ar: a heat dissipation area ^{(m 2).}

In the equation (1), the left side shows the heat value of the bearing. Ar is a constant determined from the bearing type and size. qr is a value that determines heat dissipation conditions. (1) ~
From the equation (3), in a steady state where the bearing temperature is stable, if the bearing dynamic torque and the rotation speed can be measured, the heat radiation amount can be obtained from the bearing heat generation amount. Therefore, if there is a dynamic torque measuring device capable of controlling the bearing heat radiation amount, the relationship between the bearing heat generation amount, the heat radiation amount and the bearing temperature can be quantitatively grasped. By using such a measuring device, for example, evaluate the rotation speed when the heat radiation amount, the bearing temperature, and the load have certain conditions, and the heat radiation amount, the bearing temperature, and the rotation speed have certain conditions. When the heat radiation amount is constant, the bearing temperature is evaluated when the heat radiation amount and the rotation speed and the load are under certain conditions. When the heat radiation amount is constant, a certain bearing temperature is reached. Since it is possible to evaluate the rotation speed and the load condition, it is possible to comprehensively evaluate the thermal bearing characteristics (temperature, dynamic torque) that quantitatively considers the heat radiation amount.

Regarding the above-mentioned evaluation, for example, the bearing temperature is set to a temperature at which there is a risk of seizure or the tempering temperature of the material is set. And load conditions,
It is possible to develop a bearing that quantitatively evaluates the heat dissipation conditions of the bearing (that is, develop a bearing that is unlikely to rise in temperature). The bearing temperature may be any temperature as long as it determines the bearing performance.

From the above equations (1) to (3), in order to quantitatively evaluate the heat radiation amount, it is necessary to be able to control the heat radiation condition (q) and the rotation speed (ω) with high accuracy. Recognize. In general, the rotation speed control is easy, so how to control the heat dissipation condition is an important issue in performing a highly accurate measurement test.

[0007]

A conventional example of a dynamic torque measuring device capable of temperature control is, for example, Japanese Patent Laid-Open No. 1-244.
Although disclosed in No. 332, etc., this is intended to control the refueling temperature and the ambient temperature to a constant value,
It cannot be said to be a technique for evaluating the relationship between quantitative heat dissipation control and bearing performance.

FIG. 1 shows a conventional example of a bearing dynamic torque tester for the purpose of controlling heat radiation. FIG. 1A is a front sectional view of the testing machine, and FIG. 1B is a side view thereof. In the figure, the test shaft 1 is rotatably supported by the test bearings 3 to 6 with respect to the frame 2. Bearing housing that holds the test bearings 3 to 6 (hereinafter referred to as a disk-shaped housing) 3A
6A has a disk shape having a thickness corresponding to the width of the bearings 3-6.

The test shaft 6 is connected to a drive shaft 8 via a coupling 7. The drive shaft 8 is rotationally driven by a rotary shaft of a motor 10 via a flat belt 9. Therefore, when the rotation shaft of the motor 10 rotates, the inner rings of the test bearings 3 to 6 rotate at a predetermined rotation speed.

In this test apparatus, a plurality of disk-shaped housings 3A to 6A (in this case 4
Individual pieces) are prepared and exchanged to change the heat radiation area to control the heat radiation condition from the test bearings 3 to 6 (larger diameter housing has larger heat radiation amount). However, controlling the heat radiation amount from the test bearings 3 to 6 by this method has the following problems. (1) Disc-shaped housings 3A-6 for heat dissipation control
Since A is carried out while being exchanged, setting a target heat radiation condition requires an extremely troublesome work. Therefore, the labor and time required for the test are extremely long. (2) Disk type housing 3A whose diameter is changed stepwise
~ 6A must be replaced every time the test conditions / test bearing change. Therefore, the labor and time required for assembling / disassembling and testing the testing machine are extremely long. (3) It is necessary to manufacture a plurality of disk-shaped housings 3A to 6A whose diameters are changed stepwise in order to control the amount of heat radiation, which is costly. (4) It is difficult to control the amount of heat radiation only in stages, and it is difficult to perform it precisely in a continuous manner. For high-precision control, the disk-shaped housings 3A to 6A whose diameters are changed little by little
It is necessary to prepare a large amount, and conversely, in order to save the labor of the test, if the diameter difference of the individual disk housings 3A to 6A is increased and the number thereof is reduced, the test accuracy cannot be improved. There is.

Therefore, the present invention provides a measuring device capable of accurately and easily controlling the thermal characteristics of a bearing by controlling the heat radiation amount with high precision and ease and quantitatively considering the heat radiation amount. It is an object.

[0012]

The measuring device of the present invention is characterized in that the measuring device for measuring the characteristics of the bearing is provided with control means for controlling the heat radiation amount of the bearing while operating the bearing.

[0013]

According to the measuring device of the present invention, the measuring device for measuring the characteristics of the bearing is provided with the control means for controlling the heat radiation amount of the bearing while operating the bearing. When changing the amount of heat radiation, it is possible to perform continuous tests without stopping the operation of such bearings, and it is possible to improve test efficiency.

Further, it is preferable that the control means has a supply source for supplying a temperature-controlled fluid to the support portion of the bearing. That is, in the present invention, in a measuring device for measuring the characteristics of a bearing, in order to control the amount of heat radiated from the bearing with high accuracy and ease, a liquid that is a fluid (hereinafter referred to as a cooling liquid for the sake of convenience, but a heating liquid other than cooling is used). Can also be used). The amount of heat radiated from the bearing is circulated by circulating a cooling liquid, the temperature and flow rate of which are controlled by using a temperature controller and a pump as the control means, in a housing (or a spacer) as a support portion for supporting the bearing outer ring. Can be continuously changed steplessly. In other words, it is possible to accurately and easily control the heat radiation amount, and therefore, it is possible to evaluate the thermal characteristics quantitatively considering the heat generation amount of the bearing.
Further, since the amount of heat radiation is controlled by the cooling liquid, it is not necessary to replace the housing for changing the heat radiation area after once assembling the measuring device. Therefore, the time required for assembling / disassembling and testing the measuring device can be shortened. Further, it is not necessary to manufacture a plurality of bearing housings for controlling the amount of heat radiation as in the prior art, and the cost can be reduced significantly.

However, the control means is not limited to the one that controls the heat radiation by the fluid, and the support portion may include a Peltier element, a heat pipe, a band heater, a high heat conductive material,
Provide a pipe for flowing the temperature control fluid, an oil bath, etc.
The heat radiation may be controlled.

Further, it is preferable that the support portion has a flow passage for the fluid formed therein.

[0017]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings. FIG. 2 is a schematic sectional view of the measuring device according to the present embodiment. In FIG. 2, a test shaft 101 having one end connected to a drive motor (not shown) via a torque converter 111 and a coupling 112.
Are rotatably supported with respect to the housing 102 via test bearings 103 and 104 that are spaced apart from each other.
On the other hand, the test shaft 10 between the test bearings 103 and 104
1, the load block 107 is suspended. Test bearings 105 and 106 are arranged between the load block 107 and the test shaft 101, and support them so that they can rotate relative to each other. The load block 107 is loaded downward in FIG. 2 by a load device (not shown).

The bearings 103 and 104 to be tested have ring-shaped spacers 12 having cooling passages 121a and 122a between the bearings 103 and 104 so as to abut the outer circumference of the bearings.
Cooling passages 121a, 122 in which 1, 122 are arranged
a is an inlet-side passage 102a, 10 which communicates with the connector C.
Outlet side passage 1 communicating with 2a and also communicating with connector C
It is connected to 02b and 102b. On the other hand, the test bearing 10
5, 106, ring-shaped spacers (supporting portions of the present invention: the same applies hereinafter) 123 having cooling passages 123a are arranged between them and the load block 107 so as to abut the outer circumference of the outer rings. The cooling passage 123a communicates with the inlet-side passage 107a that communicates with the connector C, and also communicates with the outlet-side passage 107b that communicates with the connector C.

FIG. 3 is a schematic diagram of a cooling system in the measuring apparatus of this embodiment. In FIG. 3, a coolant tank / pressure pump 130, which is a supply source, is connected to a flow meter 132 via a pipe 131, and the flow meter 132 is connected to a pipe 133.
It is connected to the line heater / cooler 134 via. The line heater / cooler 134 which is the control means is connected to the connector C on the inlet side. On the other hand, the connector C on the outlet side is connected to the coolant tank / pressure pump 130 via a pipe 135. PID control unit 13
6 inputs the flow rate signal from the flow meter 132, inputs the coolant temperature on the inlet side and the outlet side from the connector C using the thermocouple T, adjusts the line heater / cooler, and passes through. The temperature of the cooling fluid can be changed. still,
A similar cooling system is also provided for the spacers 122 and 23, and a description thereof will be omitted. Further, when the cooling system of the measuring apparatus is described below, the cooling system of FIG. 3 will be described as a representative.

Next, measurement using the measuring apparatus of this embodiment will be described. In FIG. 2, the test bearing 103 to
The inner ring 106 rotates with the test shaft 101 driven by a motor (not shown) via the torque converter 111.
The torque of the test bearings 103 to 106 is measured by the torque converter 111. A predetermined load is applied to the inner two test bearings 105 and 106 set on the test shaft 101 from a load device (not shown). There is.

As a reaction force at this time, a predetermined load is also applied to the two outer test bearings 103 and 104. Lubrication of the test bearings 103 to 106 can be performed by any method such as oil bath, forced circulation, and grease. Test bearing 10
The amount of heat radiation from 3 to 106 is the same as the test bearings 103 to 106.
Spacers 121, 12 inside the housing 102 in which the
2 and the cooling jackets 121a, 122a, 123a provided on the spacer 123 inside the load block 107.
Control is performed by causing a temperature-controlled cooling liquid to flow from the cooling liquid tank / pressure pump 130 of FIG. As the type of the cooling liquid, for example, water, oil, or the like that is optimum for the test may be used. More specifically, as shown in FIG. 3, from the coolant tank / pressure pump 130 to the pipe 131 and the flow meter 13
2, the pipe 133, the line heater / cooler 134, and the cooling passage 1 of the spacer 121 through the coolant through the connector C on the inlet side.
21a.

While passing through the cooling passage 121a, the spacer 1
The cooling liquid that has exchanged heat with the cooling liquid 21 is the connector C on the outlet side,
It returns to the coolant tank / pressure pump 130 via a pipe 135. Here, the amount of heat radiated from the spacer 121 to the cooling liquid is the temperature difference measured by the two thermocouples T (that is, the temperature of the cooling liquid when entering the cooling passage 121a and the temperature of the cooling liquid when leaving). It can be measured by the temperature difference.

That is, the absorbed heat quantity of the cooling liquid is obtained from the cooling liquid temperature difference between the inlet and the outlet of the spacer 121 and the cooling liquid flow rate. By insulating the test equipment from the pedestal with a heat insulating material, it can be regarded as "amount of absorbed heat of cooling liquid = amount of heat released to the outer ring side". By feeding back the result to the line heater / cooler 134 by the PID control unit 136, the heat radiation amount to the outer ring side of the test bearing can be controlled. When the bearing temperature is in a steady state, the bearing heat generation amount can be measured from the bearing dynamic torque and rotation speed.
By subtracting the heat radiation amount to the outer ring side from the total heat radiation amount), the heat radiation amount to other than the outer ring side can be quantified.

Similarly, the amount of heat radiated to the lubricating oil can be quantitatively measured by, for example, measuring the bearing inlet / outlet temperature of the lubricating oil and the oil amount during forced circulation oil supply. By doing this, it is possible to quantify the heat radiation amount to the inner ring side (shaft) by subtracting the heat radiation amount on the outer ring side and the heat radiation amount to the lubricating oil from the heat generation amount (= total heat radiation amount) of the bearing. is there. Of course, it is also possible to directly control the heat radiation amount on the inner ring side by providing a cooling jacket on the inner ring side and measuring the inlet / outlet temperature and the flow rate of the cooling liquid.

FIG. 4 is a flow chart showing the control of the cooling system. Here, when the test bearings 103 to 106 are operating under a predetermined load condition, when the temperature rise of the housing 102 or the load block 107 reaches 50 ° C., the heat radiation amount qr per unit area is, for example, 20 kW / It is assumed that m ² will be obtained in advance. In such a case, it is considered to control the temperature of the test bearings 103 to 106 to 70 ° C.

First, in step S101, as an initial value, the initial rotation speed of the test shaft 101 is set to N ₀ = 1000 rotations per minute (rpm), and the initial change amount of the rotation speed is set to dN ₀ = 1000 rotations. Set as minutes. Continuing step S
At 102, the test shaft 101 is operated at 1000 revolutions per minute and waits until the bearing temperature ΔT _brg reaches a steady state (that is, the temperature change amount is within ± 0.1 ° C.).

At this time, in step S103, the specific heat radiation amount q
If it is determined that _r does not exceed 20 kW / m ² , the process returns to step S102, and the revolutions per minute of the test shaft 101 is changed to
The rotation speed is increased by 1000 rpm, that is, the motor is operated at 2000 rpm, and the bearing temperature ΔT _{br g} is waited until it reaches a steady state (that is, the temperature change amount is within ± 0.1 ° C.).

Similarly, if it is determined in step S103 that the specific heat radiation amount q _r does not exceed 20 kW / m ² ,
Returning to step S102, the number of revolutions per minute of the test shaft 101 is increased by 1000 revolutions, that is, the test shaft 101 is operated at 3000 revolutions per minute, and the bearing temperature ΔT _{b rg} is in a steady state (that is, the temperature change amount is within ± 0.1 ° C.). ) Until.

In this way, for example, when the number of revolutions per minute of the test shaft 101 reaches 8,000 revolutions, step S10
If it is determined in 3 that the specific heat radiation amount q _r exceeds 20 kW / m ² , the process proceeds to step S104, and the specific heat radiation amount q _r is 20
If it is determined that the power consumption exceeds kW / m ² ,
The rotation speed of the test shaft 101 is decreased by 100 rotations per minute, that is, the test shaft 101 is operated at 7900 rotations per minute, and step S10 is performed.
Return to 2 and wait until the bearing temperature ΔT _brg reaches a steady state (that is, the temperature change amount is within ± 0.1 ° C.).

Further, in step S103, the specific heat radiation amount q _r
Is determined to exceed 20 kW / m ² and the specific heat radiation amount q _r is determined to greatly exceed 20 kW / m ² in step S104, the rotational speed of the test shaft 101 per minute is It is further reduced by 100 rotations, that is, it is operated at 7800 rotations per minute, the process returns to step S102, and the bearing temperature ΔT _brg is in a steady state (that is, the temperature variation is ± 0.
Wait until the temperature is within 1 ° C).

By increasing or decreasing the number of revolutions per minute of the test shaft 101 in this manner, it is determined in step S104 that the specific heat radiation amount q _r is equal to 20 kW / m ² or has exceeded within a slight amount (ε). If so, the control ends.

FIG. 5 is a schematic diagram of a cooling system in the measuring apparatus according to the second embodiment. In FIG. 5, the cooling liquid tank / pressure pump 230 is connected to the flow meter 132 via the pipe 131, and the flow meter 132 is connected to the inlet-side connector C via the pipe 134. on the other hand,
The connector C on the outlet side is connected to the coolant tank / pressure pump 230 via a pipe 135. The temperature control device 236, which is a control means connected to the heat exchanger / pressure pump 230, functions to control the temperature of the coolant supplied from the coolant tank / pressure pump 230 to the spacer 121. For example, the oilmatic series manufactured by Kanto Seiki Co., Ltd. on the market can be used.
A line heater / cooler (see FIG. 3 above) may be used instead of the temperature / temperature control device 236. Further, when the cooling liquid temperature control is hindered due to insufficient capacity of the temperature control device 236, the line heater / cooler may be used in combination with the temperature control device 236 to perform the control quickly.

FIG. 6 is a schematic diagram of a cooling system in the measuring apparatus according to the third embodiment. In FIG. 6, the coolant tank / pressure pump 230 is connected to a flow meter 132 via a pipe 131, and the flow meter 132 is connected to a connector C on the inlet side via a pipe 134. on the other hand,
The connector C on the outlet side is connected to the coolant tank / pressure pump 230 via a pipe 135. The temperature control device 236, which is a control unit connected to the cooling tank / pressure feeding pump 230, functions to control the temperature of the cooling liquid supplied from the cooling liquid tank / pressure feeding pump 230 to the spacer 121. PID receiving signal from thermocouple T
It is controlled by the control unit 136.

In the present embodiment, the thermocouple T is brought into direct contact with the bearing outer ring and the bearing temperature is monitored, so that the PID control unit 136 accurately determines the heat radiation condition satisfying "bearing temperature = target temperature". And it can be determined more easily. Although FIG. 6 shows an example in which a commercially available temperature control device 236 is used as in FIG. 4, a line heater / cooler is used instead of the temperature control device (see FIG. 3 described above).
May be used, or both may be used in combination. The target temperature is set to a temperature at which there is a risk of seizure of the bearing, or is set to the tempering temperature of the material to keep the heat dissipation conditions of the bearing constant, and then the rotational speed to reach these temperatures. By obtaining the load conditions and the load conditions, it is possible to develop bearings with higher functions (that is, bearings that are less likely to rise in temperature). The target temperature may be any temperature as long as it has a meaning that determines the bearing performance. Although the outer ring temperature is detected as the bearing temperature in the above example, the inner ring temperature may be detected by using a slip ring.

FIG. 7 is a diagram showing a spacer applicable to the above-described embodiment, FIG. 7 (a) is a front sectional view of the spacer, and FIG. 7 (b) is FIG. 7 (a). It is the figure which cut | disconnected the spacer to the VII-VII line and looked at in the arrow direction. The spacer 121 shown in FIG.
Is an annular portion 121A provided with a groove 121a in the circumferential direction, and O
Ring 121B, upper lid 121C, and a plurality of bolts 12
1D and. A coolant inlet / outlet 121b is provided on a side surface (upper surface in FIG. 7A) of the annular portion 121A. Attach an O-ring 121B for preventing coolant leakage to the seal groove 121d of the annular portion 121A, and attach the bolt 1
By fixing the upper lid 121C and the annular portion 121A at 21D, a cooling liquid jacket in which the cooling liquid flowing in the space surrounded by the groove 121a and the upper lid 121C flows is formed, and heat is generated between the cooling liquid and the inner wall. It is supposed to be exchanged.

FIG. 8 is a diagram showing a spacer according to a modification, FIG. 8 (a) is a front sectional view of the spacer, and FIG. 8 (b) is a sectional view.
It is the figure which saw the spacer of FIG.8 (a) by the VIII-VIII line, and was seen in the arrow direction. The spacer 121 'shown in FIG. 8 differs from the spacer 121 shown in FIG. 7 only in the shape of the upper lid 121C'. That is, the upper lid 121C 'has the annular portion 121
Six fins 121f are formed facing the groove 121a of A. The fins 121f are in the shape of short tubes having different radii. In this way, the fins 1 are attached to the upper lid 121C '.
By forming 21f, the groove 121a and the upper lid 121C '
The surface area in contact with the cooling liquid flowing in the space surrounded by and becomes large, and heat exchange can be performed more efficiently. The shape, direction, and material of the fin 121f can be set arbitrarily, and the site where the fin 121f is provided can be freely selected.

FIG. 9 is a perspective view showing a spacer according to another modification. In FIG. 9, the annular spacer 221 has through holes 221a penetrating in the axial direction in the same pitch circle.
Through-holes 221 that are formed and are adjacent to each other except for one place
A long-hole-shaped shallow groove 221b that connects the ends of a so as to alternate on both sides in the axial direction is provided. Therefore,
By sandwiching both end surfaces of the spacer 221 (excluding the cooling liquid inlet 221c and the outlet 221d) with a flat plate (not shown), a circulation path constituted by the flat plate and the spacer 221 is formed. By flowing the cooling liquid in the direction indicated by the arrow in the circulation path, the amount of heat radiation from the bearing (not shown) fitted inside can be controlled. By using the spacer 221 as compared with the method of forming the fin or the like, the heat radiation area can be expanded at low cost, and the heat radiation amount can be easily and efficiently controlled. It should be noted that the present invention may be applied to any method as long as it can increase the heat absorption area of the cooling liquid regardless of the above embodiment.

The following embodiment is a modification of the cooling structure for controlling the heat radiation amount. Since each modification can be applied to both housings on both sides and the center of the test apparatus shown in FIG. 2, the center housing will be described below as an example. The following modified examples can be applied to any of the above control examples.

FIG. 10 is a partial sectional view of a cooling structure for controlling the heat radiation amount of the housing by using the Peltier module. Housing 32 for holding the test bearings 105, 106
3 Peltier module 320 is arranged on the surface and a cooling effect (for example, P
Type semiconductor and metal are brought into contact with each other, and a current is applied to generate a potential difference in the contact part, and a current is applied from the semiconductor side to the metal side to generate heat absorption at the bonding part), The housing 323 can be cooled directly. Since the Peltier module 320 exhibits a cooling effect in proportion to the current and the number of chips (semiconductors) forming the Peltier module 320, the amount of heat radiation is controlled by the value of the current to be applied. When the surface of the housing 323 cannot be covered with one Peltier module 320, the heat dissipation amount can be efficiently controlled by covering the surface of the housing 323 by combining several Peltier modules 320.

FIG. 11 is a partial cross-sectional view of a cooling structure for controlling the heat radiation amount of the housing by using a heat pipe and heat radiation fins. In FIG. 11, the test bearings 105 and 106
The heat pipe 421 is installed in the vicinity of the outer periphery of the housing 423 that holds the heat pipe 421, and a part of the heat pipe 421 is projected from the housing 423.
2 is provided. The heat inside the housing 423 is transferred to the radiating fins 422 by the heat pipe 421, and the housing 423 can be cooled by forcibly cooling the radiating fins 422 with air. The amount of heat radiation is controlled by the strength of air cooling, but it is also possible to provide a liquid cooling jacket in this portion and cool with a cooling liquid. This eliminates the need to provide a cooling jacket around the outer races of the test bearings 105 and 106, and thus has the advantage of simplifying the structure around the bearing of the test apparatus and improving the disassembly and assembly of the bearing. The radiation fin 422 is provided in the housing 423.
It may be projected at both ends of. Heat pipe 421
Can be arranged on the circumference of the housing 423, thereby further increasing the heat dissipation effect.

FIG. 12 is a partial cross-sectional view of a cooling structure for controlling the heat radiation amount of the housing by using a band heater. In FIG. 12, the band heater 521 can be set to an arbitrary temperature by supplying a current from a constant voltage power source (not shown). The band heater 521 is attached to the surface of the housing 523 and the temperature is controlled to control the amount of heat radiation from the housing 523.
Such a cooling structure is effective in rapidly raising the temperature when the housing 523 is too cold, and therefore, it is preferable to provide the cooling structure together with the above-mentioned cooling jacket.

FIG. 13 is a partial cross-sectional view of a cooling structure for controlling the heat radiation amount of the housing using a high thermal conductive material. Figure 1
3 is an example in which a material 621 having a higher thermal conductivity than the material used for the housing 623 holding the test bearings 105 and 106 is attached to the surface of the housing 623 to improve the heat dissipation effect. High thermal conductivity material 62
1 includes, for example, copper, gold, silver, etc., but any material having a higher thermal conductivity than steel is effective. By devising the shape of the high thermal conductivity material 621 to be attached, the cooling effect can be improved by increasing the heat radiation area. For example, as shown in FIG. 13, a fin 621a is formed on the high thermal conductive material 621.
By attaching, the heat radiation area can be increased.
Cooling is performed by forced air cooling, but liquid cooling is also possible by providing a cooling jacket that covers the high thermal conductive material 621.

FIG. 14 is a partial sectional view of a cooling structure in which a cooling pipe is wound to control the amount of heat radiation of the housing.
In FIG. 14, a cooling pipe 721 is wound around the surface of the housing 723. The heat radiation amount control of the housing 723 is performed by changing the liquid temperature and flow rate of the cooling liquid circulating in the cooling pipe 721. By using the high thermal conductivity material described in connection with the cooling structure of FIG. 13 for the cooling pipe 721, the heat radiation effect can be further improved. It does not matter about the shape or material of the cooling pipe 721, but it goes without saying that the pipe of a long distance is in contact with the housing 723 as much as possible.
It is desirable to increase the heat transfer area. It is also effective to wind the cooling pipe 721 around the cooling structure shown in FIG.

FIG. 15 is a partial sectional view of a cooling structure for controlling the heat radiation amount of the housing using an oil bath. Figure 1
5, the cooling liquid L stored in the oil bath 821
By controlling the temperature and amount of C, the heat radiation amount of the housing 823 installed on the surface plate can be controlled. Further, by circulating the cooling liquid LC in the oil bath 821, it is possible to control the heat radiation amount of the housing 823 more efficiently. The shape and material of the oil bath 821 do not matter.

In each of the above cooling structures, an example in which a cooling structure is provided on the housing side has been shown, but if a structure capable of supplying liquid to the test shaft 101 (for example, a rotary joint manufactured by Koyo Hydraulics Co., Ltd.) is provided. It is also possible to control the heat radiation amount on the inner ring side by providing the test shaft 101 with a form similar to each cooling structure. Here, the case of the radial bearing is mainly described, but naturally the same effect is obtained also in the thrust bearing.

[0046]

According to the present invention, in order to control the heat radiation amount from the bearing in the dynamic torque measuring and testing apparatus, the heat radiation amount from the housing holding the bearing is controlled by using the cooling liquid whose temperature and flow rate are adjusted. Can be controlled with high precision and ease. As a result, it is possible to evaluate the thermal characteristics with high accuracy by quantitatively considering the heat generation amount of the rolling bearing. Since the amount of heat radiation is controlled by the cooling liquid, it is not necessary to replace the housing to change the heat radiation area once the test device is assembled. Therefore, the time required for assembling / disassembling and testing the test device can be shortened. Further, unlike the conventional example, it is not necessary to manufacture a plurality of housings for controlling the amount of heat radiation, and the cost can be significantly reduced.

[Brief description of drawings]

FIG. 1 is a view showing a conventional example of a bearing dynamic torque tester for the purpose of controlling heat radiation.

FIG. 2 is a schematic cross-sectional view of a measuring device according to the present embodiment.

FIG. 3 is a schematic diagram of a cooling system in the measuring device according to the present embodiment.

FIG. 4 is a flowchart showing control of a cooling system.

FIG. 5 is a schematic diagram of a cooling system in the measuring apparatus according to the second embodiment.

FIG. 6 is a schematic diagram of a cooling system in the measuring apparatus according to the third embodiment.

FIG. 7 is a diagram showing a spacer applicable to the above-described embodiment, FIG. 7 (a) is a front sectional view of the spacer, and FIG.
[Fig. 7] is a view of the spacer of Fig. 7 (a) taken along line VII-VII and viewed in the direction of the arrow.

8 is a diagram showing a spacer according to a modified example, and FIG.
FIG. 8A is a front sectional view of the spacer, and FIG.
It is the figure which cut | disconnected the spacer of (a) by the VIII-VIII line, and was seen in the arrow direction.

FIG. 9 is a perspective view showing a spacer according to another modification.

FIG. 10 is a partial cross-sectional view of a cooling structure that controls a heat radiation amount of a housing using a Peltier module.

FIG. 11 is a partial cross-sectional view of a cooling structure that controls a heat radiation amount of a housing by using a heat pipe and heat radiation fins.

FIG. 12 is a partial cross-sectional view of a cooling structure that controls a heat radiation amount of a housing using a band heater.

FIG. 13 is a partial cross-sectional view of a cooling structure that controls a heat radiation amount of a housing by using a high thermal conductive material.

FIG. 14 is a partial cross-sectional view of a cooling structure in which a cooling pipe is wound to control the heat radiation amount of the housing.

FIG. 15 is a partial cross-sectional view of a cooling structure that controls the heat radiation amount of the housing using an oil bath.

[Explanation of symbols]

101 test axis 103, 104, 105, 106 Test bearings 121,221,321 134 Line heater / cooler 136 PID control unit

─────────────────────────────────────────────────── ─── Continuation of front page (51) Int.Cl. ⁷ Identification code FI theme code (reference) // F16C 37/00 F16C 37/00 B (72) Inventor Kazutoshi Sakaguchi Kamei Kugenuma, Fujisawa City, Kanagawa Prefecture No. 5-50 NSK Ltd. (72) Inventor Yuji Shimomura 1-5-50 Kumei Kugenuma, Fujisawa City, Kanagawa Prefecture No. 50 NIPPON SEIKO CO., LTD. (72) Hironari Sakoda 1-5, Shinmei Kugenuma, Fujisawa, Kanagawa No. 50 F-term within NSK Ltd. (reference) 2F056 YF02 YF06 2G024 AC01 BA11 CA17 DA16 3J017 EA02 FA01 GA01 3J101 AA01 AA32 FA22 GA60

Claims (3)

[Claims] 1. A dynamic characteristic measuring device for a rolling bearing, comprising: a measuring device for measuring a dynamic characteristic of a rolling bearing; and a control means for controlling a heat radiation amount of the bearing while operating the bearing. 2. The dynamic characteristic measuring device for a rolling bearing according to claim 1, wherein the control means has a supply source for supplying a temperature-controlled fluid to the support portion of the rolling bearing. 3. The dynamic characteristic measuring device for a rolling bearing according to claim 2, wherein the support portion has a passage for the fluid formed therein.